Variable pitch bladed disc

ABSTRACT

A variable pitch bladed disc including a plurality of blades, each being of variable pitch about a blade axis of rotation and having a root, the plurality of blades including at least one first blade and at least one second blade, a plurality of rotor connecting shafts, each shaft having a root and a tip, the root of each blade being mounted on the tip of a corresponding rotor connecting shaft via a pivot so as to allow each blade to be rotated about the blade axis of rotation, the first blade having a first rotation axis inclination such that the rotation axis thereof is inclined in a fixed manner with respect to a radial axis passing through the root of the corresponding shaft, and the second blade has a second rotation axis inclination different from the first rotation axis inclination.

FIELD OF THE INVENTION

The invention relates to a variable pitch bladed disc, as well as to aturbine engine comprising such a variable pitch bladed disc.

STATE OF THE ART

Turbine engine bladed wheels comprising at least one rotor and bladeswith variable geometrical pitch, are known from the state of the art.

In the case of propeller-driven engines with one or several propellers,each propeller comprises a plurality of blades of a bladed wheel, theblades being positioned circumferentially to the periphery of the bladedwheel, the blades having the same geometrical configuration around theaxis of the turbine engine or the axis of the propeller, the bladesbeing driven into rotation by the rotor around this axis.

The system of blades with variable pitch gives the possibility ofmodifying the pitch of all the blades in an identical way so as to adaptthe aerodynamic operation of the blades of the propeller to thevariation of the flight conditions. This variation may result eitherfrom a change in the flight point pair (z altitude, Mn Mach) or in therotary condition of the propellers.

The propeller engine is for example a motor of the turboprop type.

This may also be an engine of the “open rotor” or “unducted fan” type,typically with an unducted fan and with contra rotative open rotor. Thefan of a turbine engine of this type typically comprises two coaxialexternal propellers corresponding to two bladed wheels, respectivelyupstream and downstream, at least one of which is driven into rotationand which extend substantially radially outside the nacelle of thisturbine engine, so as to have different speeds of rotation. For example,only one of the propellers may be driven, or the propellers may becontra rotative.

The geometrical pitch is typically the angle formed by the cord of theprofile of the blade and the plane of rotation of the propeller, definedas the plane orthogonal to the axis of rotation of the propeller of thebladed wheel.

For this purpose, as illustrated in FIG. 1, a rotor is known comprisingfor each blade 2 of the propeller a radial shaft 6, a head 601 of whichis bound to the blade 2 through a pivot 8 on which is housed a root ofthe blade 201.

The rotation of the radial shaft 6 may be controlled by the axialdisplacement of a connecting rod 9. An actuator (not shown) may controlthe axial displacement of the control rods 9, and thus adjust in auniform way the pitch of the set of the blades 2 so as to systematicallyobtain the same pitch for all the blades.

The acoustic certification of an airplane is based on the EPNL(“Effective Perceived Noise Level”) criterion, which aims at evaluatingthe noise levels of the airplane in the approach and take-off phases.

The EPNL also takes into account the discomfort perceived by the humanear, and caused by the different measured components of the noisespectra.

The propeller engines, as described above, generate for the human ear asignificant noise during the approach and take-off phases, which limitstheir possibility of acoustic certification and therefore theirapplication.

GENERAL PRESENTATION OF THE INVENTION

A goal of the invention is to propose a bladed wheel with variable pitchgiving the possibility of reducing the effective noise perceived by anobserver on the ground during the take-off and approach phases at a lowspeed and produced by the turbine engine during operation.

In order to overcome the drawbacks of the state of the art, theinvention proposes a bladed wheel with variable pitches comprising:

-   -   a plurality of blades, each with a variable pitch along an axis        of rotation of a blade and each having a root, the plurality of        blades comprising at least one first blade and at least one        second blade,    -   a plurality of rotor connection shafts, each shaft having a foot        and a head, the root of each blade being mounted on the head of        a corresponding rotor connection shaft through a pivot so as to        allow the rotation of each blade along the blade rotation axis,

wherein the first blade has a first tilt of the axis of rotation, suchthat the blade rotation axis of the first blade is tilted in a fixed waywith respect to a radial axis of the bladed wheel passing through thefoot of the corresponding shaft, and the second blade has a second tiltof the axis of rotation different from the first tilt of the axis ofrotation.

Such a bladed wheel gives the possibility of reducing the noise producedby the turbine engine during operation and perceived by the human ear.

Indeed, the global noise produced by an operating airplane comprises afirst tone component, generated by the rotating portions of the airplaneand/or by mechanisms generating vortices, and a second wide bandcomponent mainly generated by the interaction of turbulent structures(for example in the presence of a vortex or of wakes, typically at thelimiting layers) with the bearing surfaces of the airplane.

The emergence of acoustic levels of lines of the first tone componentwith respect to the noise of the second wide band component causes astrong discomfort perceived by the human ear. Such an emergence is thusa strong penalty during the evaluation of the EPNL criterion.

When all the blades are distributed in a uniform way on the blading,like in existing engines, the specific noise of the bladed wheel thusconsists of the fundamental line and of its harmonics.

The bladed wheel according to the invention has at its circumference amodified periodicity of the distribution of the blades, so as todistribute the acoustic energy making up the specific noise on severaldistinct frequencies.

The invention thus gives the possibility of reducing the emergence oflines of the specific noise of the bladed wheel with respect to the wideband level, and therefore of reducing the calculated EPNL levels as wellas the perceived discomfort.

The invention is advantageously completed by the following features,taken alone or in any of their technically possible combinations:

-   -   the first tilt of the axis of rotation comprises a tangential        tilt component in the plane of the bladed wheel;    -   the first tilt of the axis of rotation comprises a tilt        component towards the upstream or the downstream side with        respect to the plane of the propeller;    -   each shaft corresponding to a first blade is tilted with respect        to the radial axis, tilting the first corresponding blade        according to the first tilt of the axis of rotation,    -   each shaft corresponding to a first blade has a joint tilting        the head of the shaft with respect to the remainder of the        shaft, and thus tilting the first corresponding blade according        to the first tilt of the axis of rotation;    -   the first blade and the second blade have the same geometrical        shape;    -   the first blade has a first blade tilt, such that the first        blade is tilted in a fixed way with respect to the blade        rotation axis of the first blade, and the second blade has a        second blade tilt different from the first blade tilt;    -   the first blade and the second blade are configured so that the        respective pitches along the corresponding blade axes of        rotation are modified simultaneously, and so that:        -   when the bladed wheel is blocked in a high speed position,            the position of the first blade with respect to the            corresponding radial axis is the same as the position of the            second blade with respect to the corresponding radial axis,        -   when the bladed wheel is blocked in a low speed position,            the position of the first blade with respect to the            corresponding radial axis is different from the position of            the second blade with respect to the corresponding radial            axis.

The invention also relates to a turbine engine comprising such a firstbladed wheel.

The invention is advantageously completed by the following features,taken alone or in any of their technically possible combinations:

-   -   a second bladed wheel, the second bladed wheel comprising a        plurality of blades, the first bladed wheel being positioned        upstream or downstream from the second bladed wheel along the        axis of the turbine engine, so as to allow, during the operation        of the turbine engine, a time and/or space phase shift of        -   the interaction between the first blade of the first bladed            wheel and the blades of the second bladed wheel, with        -   the interaction between the second blade of the first bladed            wheel and the blades of the second bladed wheel;    -   both bladings have different speeds and/or directions of        rotation.

SHORT DESCRIPTION OF THE FIGURES

Other features and advantages of the invention will become apparentduring the description hereafter of an embodiment. On the appendeddrawings:

FIG. 1 is a partial illustration of a bladed wheel of the prior art;

FIG. 2 is a partial illustration of a turbine engine on which the bladedwheel is able to be integrated;

FIG. 3a is a schematic illustration of a first tilt of a tangential axisof rotation in the plane of the propeller of a bladed wheel according toan exemplary embodiment of the invention;

FIG. 3b is a schematic illustration of a first blade tilt of a bladedwheel according to exemplary embodiment of the invention;

FIG. 3c is a schematic illustration of a bladed wheel according toanother exemplary embodiment of the invention;

FIG. 3d is a schematic illustration of a bladed wheel according toanother further exemplary embodiment of the invention;

FIG. 4 schematically illustrates the specific lines of the acousticradiation of a bladed wheel according to the prior art with respect tothe bladed wheel of FIG. 3 d;

FIG. 5 illustrates a detail of a bladed wheel comprising a connectingshaft tilted according to another further exemplary embodiment of theinvention;

FIG. 6 illustrates a detail of a bladed wheel comprising bellowsaccording to another further exemplary embodiment of the invention;

FIG. 7 illustrates a detail of a bladed wheel comprising a universaljoint according to another further exemplary embodiment of theinvention;

FIG. 8 illustrates a detail of a second blade of a bladed wheelaccording to an exemplary embodiment of the invention;

FIG. 9 illustrates a detail of a bladed wheel comprising a blade tiltaccording to another further exemplary embodiment of the invention;

FIG. 10 illustrates a detail of a bladed wheel comprising a tilt of theaxis of rotation and a blade tilt according to another further exemplaryembodiment of the invention;

FIG. 11 is a partial illustration of a turbine engine with contrarotative bladings indicating sources of interaction noise between thebladings;

FIG. 12 schematically illustrates bladed wheels according to the priorart and according to exemplary embodiment of the invention;

FIG. 13a schematically illustrates a blade seen as a profile; and

FIG. 13b schematically illustrates a sectional view of a section of theblade of FIG. 13 a.

DETAILED DESCRIPTION OF THE INVENTION

Turbine Engine

With reference to FIG. 2, a turbine engine portion 12 is illustrated.The turbine engine 12 is typically a turboprop.

The turbine engine 12 typically comprising a fan 3, in which the vanesor blades 2 belong to at least one bladed wheel, for example a simplepropeller (not shown) or two propellers, typically two contra rotativepropellers.

By bladed wheel, is meant for example a set of blades, distributed overa same ring, the ring extending around the engine axis.

The blades are for example distributed in a regular way in azimuth, forexample with a tangential spacing of 2π/N_(blades) radians whereinN_(blades) is the number of blades of the bladed wheel.

In the case of an engine with a simple propeller, the propelling systemconsists of a single propeller.

In the case of an engine with several wheels, this is for example aturbine engine of the “open rotor” or “unducted fan” type, typicallysuch a turbine engine with contra rotative bladings.

Conventionally, an air flow at a high pressure and temperature withrespect to the external flow to the engine gives the possibility ofdriving into rotation the rotor 5.

The rotor 5 then has a movement of rotation around a longitudinal axisA₄ of the fan 3, which is transmitted to the blades 2 of the simplewheel or of the wheels, for their setting into rotation around alongitudinal axis A₄.

Blading

Variable Pitch

With reference to FIGS. 5 to 10, bladed wheels 1 comprising blades 2according to the invention are described.

As stated earlier, the geometrical pitch is for example the angle formedby the cord of the profile of a blade 2 and the plane of rotation of thecorresponding propeller 4. Subsequently, only the term “pitch” will beused, as this is currently used in the state of the art.

It is noted that the pitch is an algebraic value. For example, a −90°pitch corresponds to a pitch for which the leading edge of the blade 2is located rearwards.

The pitch of the blades 2 of the bladed wheel or of the propeller isadapted according to the flight conditions: for example, on the ground,the pitch is close to 10°, upon take-off, between 35° and 45°, and uponascent, between 45° and 60°. During cruising, the pitch is close to 65°.

The 90° pitch is conventionally designated as a “feather” position byone skilled in the art, the 0° pitch, a “flat” position, and the −30°pitch, the “reverse” position (this position gives the possibility ofbreaking the aircraft).

The bladed wheel 1 comprises a plurality of blades 2 of the bladed wheelor propeller blades. Each blade 2 is with variable pitch along a bladerotation axis A₁. Each blade 2 has a root 201.

The plurality of blades 2 comprises at least one first blade 21 and atleast one second blade 22. The plurality of blades 2 thus comprises oneor several first blades 21 and one or several second blades 22.

The bladed wheel 1 comprises a plurality of shafts 6 for connection tothe rotor. Each connecting shaft 6 is typically adapted so that itsrotation modifies the pitch of one of the blades 2. Each connectingshaft 6 has a foot 602 and a head 601. The shafts 6 are for examplepositioned at a rotating case arm 702, between a vein coming from theturbine 701 and a vein directed towards the nozzle 703.

The root 201 of each blade 2 is typically mounted on the head 601 of arotor connecting shaft 6.

Conventionally, each blade 2 is bound to the corresponding connectingshaft 6 through a dedicated pivot 8 so as to allow the rotation of eachblade 2 along the blade 2 axis of rotation A₁. The root 201 of eachblade 2 is for example mounted on the head 601 of a rotor connectingshaft 6 via the pivot 8. The pivot 8 may comprise counterweights 801.Thus the root 201 of the blade 2 may be housed in the pivot 8. Thepivots 8 are for example mounted in an axisymmetrical ring 802 having aplurality of substantially cylindrical radial housings, this ring 802being currently designated as a polygonal ring. Roller bearings 803positioned between the polygonal ring 802 and the pivot 8 give thepossibility of retaining a degree of rotary freedom of the pivot 8 withrespect to the polygonal ring 802.

The bladed wheel may further comprise parts able to be displacedtogether along an axial direction so as to drive into rotation theconnecting shaft 6. The parts generally comprise a connecting rod 9, oneend of which is connected to the connecting shaft 6. Each connecting rod9 is connected to a connecting shaft 6 of a blade 2.

The device 1 may further comprise at least one actuator (not shown)controlling the displacement of the connecting rod 9 along the axialdirection.

The pitch of the blade 2 may be modified by axial extension of the rodof the actuator, which acts on the connecting rod 9 in an axialtranslation.

Tilt of the Axis of Rotation

The first blade 21 has a first tilt of the axis of rotation, such thatits blade rotation axis A₁ is tilted in a fixed way with respect to aradial axis A₂, the radial axis A₂ passing through the foot 602 of thecorresponding shaft 6, i.e. the shaft 6 is adapted so that its rotationmodifies the pitch of the first blade 21. The first tilt of the axis ofrotation is non zero because of its tilt with respect to the radial axisA₂.

The second blade 22 has a second tilt of the axis of rotation, typicallywith respect to the radial axis A₂, which is different from the firsttilt of the axis of rotation. The axis of rotation of the second blade22 is typically tilted in a fixed way with respect to the correspondingradial axis A₂.

Thus, the second tilt of the axis of rotation may be such that thecorresponding blade rotation axis A₁ has zero tilt, i.e. its bladerotation axis A₁, is not tilted with respect to the radial axis A₂passing through the foot 602 of the corresponding shaft 6, i.e. theshaft 6 is adapted so that its rotation modifies the pitch of the secondblade 22, the second blade 22 being mounted so that its lack of tilt ismaintained.

Alternatively, the second blade 22 may be mounted so as to have a bladerotation axis A₁ tilted in a fixed way with respect to the radial axisA₂ passing through the foot 602 of the corresponding shaft 6, i.e. theshaft 6 is adapted so that its rotation modifies the pitch of the secondblade 22, the second tilt of the axis of rotation being however brokendown into components having values different from those of the firsttilt of the axis of rotation, i.e. that at least one of the componentsdoes not have the same value for the tilt of the axis of rotation of thefirst blade and for the tilt of the axis of rotation of the secondblade.

A tangential tilt component and/or a tilt component towards the upstreamside or towards the downstream side with respect to the plane of thepropeller is thus typically different from the corresponding componentof the first tilt of the axis of rotation. The result of this is anuntuning between said at least one first blade 21 and said at least onesecond blade 22 for at least one pitch. By untuning, is meant that theblades of a same bladed wheel, are no longer governed by cyclic symmetryby rotation by a constant angle around the engine axis. By constantangle around the engine axis, is meant an angle equal to 360/N degreeswherein N represents the number of blades of the wheel.

Such a bladed wheel gives the possibility of reducing the effectiveperceived noise produced by the operating turbine engine.

Indeed, the global noise produced by an airplane during operationcomprises a first tone component, generated by the rotating portions ofthe airplane and/or by mechanisms for generating a vortex, and a secondwide band component mainly generated by the interaction of turbulentstructures with the bearing surfaces of the airplane.

As indicated earlier, the acoustic certification of an airplane is basedon the EPNL criterion, which is representative of the noise levels ofthe airplane in the approach and take-off phases. The EPNL also takesinto account the discomfort perceived by the human ear, and caused bythe different components, the tone component and the wide bandcomponent, of the measured noise spectra.

The emergence of the acoustic levels of lines of the first tonecomponent with respect to the noise level of the second wide bandcomponent causes strong discomfort perceived by the human ear. Such anemergence is therefore a strong penalty during the evaluation of theEPNL criterion.

The specific noise of a propeller for example radiates at rotationfrequencies which are multiples of the speed of rotation and of thenumber of blades uniformly distributed over the bladed wheel. Suchfrequencies are thus of the form k.ω.N, wherein k is an integer, ω thespeed of rotation, for example expressed in Hertz or in revolutions/s,and N the number of uniformly distributed blades. Such frequencies arecalled blade passing frequencies (BPF).

Thus, for the i^(th) bladed wheel comprising N_(i) blades and rotatingat a rotation condition in turns/min RPM_(i), a blade passing frequencyof the i^(th) BPF_(i) wheel is obtained by a formula of the type:BPF_(i) =N _(i)*RPM_(i)/60

When all the blades are distributed uniformly over the bladed wheel orpropeller, like in existing engines, the specific noise of the propellermay thus consist of the fundamental line at the frequency BPF_(i) and ofits harmonics.

Thus, the acoustic contributions of each blade, over the total specificnoise of the bladed wheel, are added in amplitude and in phase and theamplitude of the radiated specific noise is mainly proportional to theglobal load of the bladed wheel and of the displaced fluid volume. Eachblade thus contributes for example to a fraction of the global tractionaccording to a formula of the type:T _(j) =T/N _(j)wherein T_(j) is the traction generated by the j^(th) blade, T is theglobal traction and N_(i) is the number of blades of the i^(th) bladedwheel.

When the blades are uniformly distributed in azimuth on the propeller,the radiated acoustic energy is localized at the frequencies n*BPFi ofthe rotation.

The bladed wheel according to the invention has a modified periodicitybecause of the tilt of the axis of rotation of the first blade 21 or ofthe first blades 21 which is different from the tilt of the axis ofrotation of the second blade 22 or of the second blades 22, so as todistribute for a given pitch the acoustic energy making up the specificnoise over several distinct frequencies and to obtain untuning infrequency.

By considering for example loads distributed in the same way betweeneach of the blades, the described heterogeneous bladed wheel, which hasa modified bladed wheel periodicity from one blade to the other for atleast one pitch, because of the tilt of the axis of rotation,preferentially tangentially in azimuth, alternatively or additionallytowards the upstream side or towards the downstream side with respect tothe plane of the propeller, contributes to distributing the acousticenergy making up the specific noise over several distinct frequencies.The upstream and downstream sides are typically defined with respect tothe upstream side and to the downstream side of the engine.

The invention thus allows reduction in the emergence of lines of thespecific propeller noise with respect to the wide band level, andtherefore reduction in the calculated EPNL levels as well as theperceived discomfort.

As illustrated in FIG. 3a , the first tilt of the axis of rotation maycomprise a tangential tilt component β in the plane of the bladed wheel,i.e. such a non-zero component. The tangential direction is typicallydefined by the plane of rotation around the engine shaft.

Alternatively or additionally, as illustrated in FIGS. 5, 6 and 7, thefirst tilt of the axis of rotation may comprise a tilt component towardsthe upstream side or towards the downstream side a with respect to theplane of the bladed wheel, i.e. such a non-zero axial component.

By plane of the bladed wheel or plane of the propeller, is meant forexample the plane orthogonal to the axis of the turbine engine at whichis positioned the bladed wheel. The plane of the bladed wheel is thusfor example the plane in which substantially extends the bladed wheel.This is then the plane orthogonal to the engine axis and in which islocated the center of gravity of the bladed wheel.

By convention, a will be considered as positive for anupstream-downstream tilt towards the upstream side and β will beconsidered positive for a tangential tilt in the direction defined bythe rotation of the propeller, typically around the engine shaft, i.e.towards the intrados.

In the same way, the second tilt of the axis of rotation may comprise atangential tilt component β in the plane of the propeller, i.e. such anon-zero component, and/or a tilt component α towards the upstream sideor towards the downstream side with respect to the plane of thepropeller, i.e. such a non-zero component.

Alternatively, as indicated earlier, the second tilt of the axis ofrotation may comprise a zero tangential tilt in the plane of thepropeller, and/or a zero tilt towards the upstream side or towards thedownstream side with respect to the plane of the propeller asillustrated in FIG. 8.

The blade rotation axis A₁ of the first blade 21, optionally of thesecond blade 22, is typically tilted in a fixed way with respect to thecorresponding radial axis A₂. The tangential tilt component β and/or theα tilt component towards the upstream side or towards the downstreamside of the first tilt of the axis of rotation, optionally of the secondtilt of the axis of rotation, may be fixed with respect to the radialaxis A₂. In other words, the tilt of the axis of rotation of the firstblade 21, optionally of the second blade 22, may be set with respect tothe radial axis A₂ so as to only allow, during the operation of theblading, a rotation of the first blade 21, optionally of the secondblade 22, along the corresponding blade rotation axis A₁, the axis ofrotation A₁ being thus tilted tangentially and/or towards the upstreamside or towards the downstream side in a fixed way with respect to thecorresponding radial axis A₂. Thus, the blade 2 only has one degree offreedom in rotation, typically a degree of freedom in rotation along asingle axis, that along the axis of rotation A₁, no rotation along otheraxes of rotation being possible.

The tangential tilt component β and/or the α tilt component towards theupstream side or towards the downstream side, in other words thetangential tilt angle and the tilt angle towards the upstream side ortowards the downstream side are for example determined during thedesign, and may therefore be set by the building of the bladed wheel.

Thus, during the design process, the combination of the α tilt componenttowards the upstream side and the β tangential tilt component isdetermined for meeting determined aero-acoustic and mechanical goals.

This combination of a tilt component towards the upstream side a and ofthe tangential tilt component β, i.e. this combination of angles, isthen for example applied to the roller bearings 803. The only remainingdegree of freedom is then the angle of rotation of the blade 2, forexample of the first blade 21 and/or of the second blade 22, around theaxis which is defined by the roll (and which is controlled by thecontrol for changing pitch via the radial shaft). The angles α and β arefor example set at the manufacturing of the ring 802. As illustrated inFIG. 5, each connecting shaft 6 corresponding to a first blade 21,optionally to a second blade 22, may be tilted with respect to theradial axis A₂, thereby tilting the first blade 21, optionally thesecond blade 22, corresponding according to the desired tilt of the axisof rotation. Such an application is particularly suitable for tilt forwhich the tangential components and towards the upstream or downstreamside do not exceed 5° in absolute value.

The tilt of the connecting shaft 6 corresponding to the ant first blade21, optionally to the second blade 22, is for example a set tilt withrespect to the corresponding radial axis A₂, typically at a tiltcomprising a tangential component β and/or the tilt component towardsthe upstream or towards the downstream side α fixed with respect to theradial axis A₂.

Alternatively, or additionally, each connecting shaft 6 of the rotorcorresponding to the first blade 21, optionally to a second blade 22,may have a joint tilting the head 602 of the connecting shaft withrespect to the remainder of the shaft 6, and thus tilting the firstblade 21, optionally the second corresponding blade 22, according to thedesired tilt of the axis of rotation.

The joint may maintain the head 602 of the shaft according to a tiltfixed with respect to the radial axis A₂, typically a tilt comprising atangential component β and/or the tilt component α towards the upstreamside or towards the downstream side which is fixed with respect to theradial axis A₂.

With reference to FIG. 6, such a joint may comprise bellows 10, forexample metal bellows. Such bellows 10 are adapted for applying a firsttilt of the axis of rotation, optionally a second tilt of the axis ofrotation, the components of which may have values of several degrees.

With reference to FIG. 7, such a joint may comprise a universal joint11. Such a universal joint 11 is suitable for applying a first tilt ofthe axis of rotation, optionally a second tilt of the axis of rotation,the components of which may have values of several tens of degrees.

The first blade and the second blade for example have the samegeometrical shape. Thus, the tilt difference of the axis of rotationbetween the first blade 21 or the first blades 21 and the second blade22 or the second blades 22 gives the possibility of reducing the noiseproduced by the bladed wheel while having the same geometrical shape forall the blades. The result of this is more easy dimensioning since it isnot necessary to produce the bladed wheel with two types of differentblades, and therefore a reduction in the development and productioncosts of the bladed wheel.

The mechanical performances may also be improved by a first and/orsecond tilt of the axis of rotation comprising a tilt component towardsthe upstream side or towards the downstream side α with respect to theplane of the propeller.

Moreover, the bladings are caused to operate under various aerodynamicconditions according to the flight points such that the take-off, theascent or the cruising. It is known that these different flight pointsimply different geometries of a bladed wheel by variation of the pitch.

The variation of pitch by rotation of the blades 2 according to theprior art limits the possibilities of compromise on a geometry of thebladed wheel adapted for the different flight points.

The introduction of a first tilt of the axis of rotation, and optionallyof a second tilt of the axis of rotation, also allows improvement in theaerodynamic performances of the bladed wheel. The first and/or secondtilt of the axis of rotation allows improvement in the pitch variationsbetween the root 201 of the blade and a head of the blade 2 and thuspossible re-adaptation of the tilt of the flow on the profiles over therelevant span of the blade.

One skilled in the art will understand that by a different tilt of theaxis of rotation, is meant a difference going beyond the uncertaintiesspecific to this type of technical manufacturing. On the contrary, twotilts of the axis of rotation having differences in the order ofmagnitude of these uncertainties are considered by one skilled in thepart as being identical, and cannot obtain the technical effectsdiscussed herein before.

The difference in absolute value between the first tilt of the axis ofrotation and the second tilt of the axis of rotation is for example ofthe order of one degree, for example greater than or equal to 1°, forexample greater than or equal to 2°, for example greater than or equalto 4°, for example greater than or equal to 5°.

Blade Tilt with Respect to the Axis of Rotation

Each blade of the bladed wheel may have a fixed position with respect tothe blade rotation axis A₁ of the relevant blade in the rotatingreference system of the relevant blade. This position for examplecorresponds to a tilt which may be zero or non-zero.

All the blades may thus be tilted in a fixed way with respect to theirrespective axes of rotations according to respective blade tilts.

By blade tilt, is typically meant the angle in an algebraic value,formed between the axis of stacking of the relevant blade and the axisof rotation of the relevant blade. Each blade is for example formed witha plurality of blade sections stacked so as to form said blade. Eachsection for example extends between a leading edge and a trailing edge.The stacking axis may thus be defined as the axis passing through thecenters of gravity of the blade sections forming the relevant blade.

If the centers of gravity cannot be connected through a straight line,the stacking axis may be a stacking curve. This stacking curve has atangent at the end located at the root of the blade, which thuscorresponds to the intersection of the stacking curve and of a hub ofthe nacelle of the turbine engine. The blade tilt may then be defined asthe angle in an algebraic value, formed between said tangent of therelevant blade and the axis of rotation of the relevant blade.

The blade tilts of the first blade 21 and of the second blade 22 may beidentical, for example zero or non-zero. In this case, if the firstblade 21 and the second blade 22 have identical shapes and differenttilts of the axis of rotation, regardless of the pitch, the bladed wheelexhibits untuning.

Alternatively or additionally to the difference of tilt of the axis ofrotation between the first blade 21 and the second blade 22, the firstblade 21 may have a first blade tilt, such that the first blade 21 istilted in a fixed way with respect to the blade rotation axis A₁ of thefirst blade 21, and the second blade 22 may exhibit a second blade tiltdifferent from the first blade tilt.

The result of this is an untuning between said at least one first blade21 and said at least one second blade 22 for at least one pitch. Byuntuning, is meant that the blades of a same bladed wheel, are no longergoverned by a symmetry by rotation of a constant angle around the engineaxis.

In the same way as for the untuning obtained by difference of tilt ofthe axis of rotation as described herein before, such a bladed wheelgives the possibility of reducing the effective perceived noise producedby the operating turbine engine.

Indeed, the bladed wheel according to the invention has a periodicitymodified because of the blade tilt of the first blade 21 or of the firstblades 21 which is different from the blade tilt of the second blade 22or of the second blades 22, so as to distribute for a given pitch, theacoustic energy making up the specific noise on several distinctfrequencies and to obtain untuning

For example by considering the loads distributed in the same way betweeneach of the blades, the described heterogeneous bladed wheel which has amodified periodicity of a bladed wheel from one blade to the other forat least one pitch, because of the tilt of the blade axis for at leastone pitch, contributes to distributing the acoustic energy making up thespecific noise over several distinct frequencies.

The invention thus gives the possibility of reducing the emergence ofthe lines of the specific propeller noise with respect to a wide bandlevel, and therefore of reducing the calculated EPNL levels as well asthe perceived discomfort.

As illustrated in FIG. 3b , the first blade axis tilt, i.e. the tilt ofthe cord A₃ of the profile of the blade with respect to the axis ofrotation A₁ may comprise a tangential tilt component in the plane of thebladed wheel for a given pitch, i.e. such a non-zero component.Depending on the time-dependent change in the pitch, i.e. of therotation of the blade with respect to its axis of rotation, thiscomponent may alternatively be tangential, towards the upstream side ortowards the downstream side. FIG. 9 thus illustrates for example a firstblade 21, for which the cord A₃ is tilted with respect to the axis ofrotation A₁, thus tilting the first blade 21 according to the desiredblade tilt.

By rotating reference system of a blade, is meant the reference systembound to the blade and in which this blade is therefore fixed.

One skilled in the art will understand that by different blade tilt ismeant a difference going beyond specific uncertainties of this type oftechnical manufacturing. On the contrary, two blade tilts havingdifferences of the order of magnitude of these uncertainties areconsidered by one skilled in the art as being identical, and cannotobtain the technical effects discussed herein before.

The difference in absolute value between the first blade tilt and thesecond blade tilt is for example of the order of one degree, for examplegreater than or equal to 1°, for example greater than or equal to 2°,for example greater than or equal to 4°, for example greater than orequal to 5°.

The representation of a blade in the form of a plurality of stackedblade sections is a standard representation for one skilled in the art.Also, it is standard for one skilled in the art, from such arepresentation, to determine the center of gravity of a blade section,which depends in a standard way on the distribution of the constitutivematerial(s) of the section and of the shape of the relevant section.Alternatively, the computed center of gravity may be a center of gravityin the geometrical sense of the term, i.e. that the distribution of thematerial(s) is not taken into account and that the center is computed onthe only basis of the relevant section shape, as if a single materialwas distributed in a homogenous way.

With reference to FIG. 13a , a blade 2 schematically illustrated as aprofile view is described. The blade 2 is formed with a plurality ofblade sections. FIG. 13b schematically illustrates a sectional view of asection 3100 of the blade of FIG. 13a along the plane W-W′. The section3100 extends between a leading edge 3110 and a trailing edge 3120 andhas a center of gravity 3130, which here corresponds both with thegeometrical center of gravity and with the center of gravity in themechanical sense in the case of a blade in a homogeneous material. Thestacking curve 3200 thus corresponds to the curve passing through thecenters of gravity of the blade sections forming the relevant blade. Theblade tilt 3400 may then be evaluated by considering the tilt of thetangent 3300 to the curve located at the root 201 of the blade 2 withrespect to the axis of rotation of the blade A₁.

The angle in an algebraic value may be expressed according to themethods conventionally used by one skilled in the art. The tilt may bebroken down into three rotations by the method of the Euler angles, eachrotation being expressed by an algebraic value. Choice of the sign forthe algebraic value may be made according to any convention known to oneskilled in the art.

Tilt of the Axis of Rotation and Blade Tilt

The first blade 21 and the second blade 22 may be configured so thattheir respective pitches along the axis of rotation are modifiedsimultaneously.

The first blade and the second blade may be configured for exhibitingdifferent tilts of the axis of rotation and different blade tilts. Sucha combination of the two differences in tilt allows more accuratedimensioning of the bladed wheel according to the untuning to beobtained.

In particular, the first blade and the second blade may be configuredfor having different tilts of the axis of rotation and different bladetilts so that in a first pitch position, for example when the bladedwheel is blocked in a high speed position, the first blade and thesecond blade each have the same position with respect to thecorresponding radial axes, and so that in a second pitch position, forexample a low speed position, the first blade and the second blade havedifferent positions with respect to the corresponding radial axes.

Thus it is possible, by retaining the same geometrical shape of theblade 2, to obtain a blading for which the noise during the operationupon take-off and on landing is reduced while retaining its efficiencyin operation at a high altitude for which the positioning of the bladeswithin the bladed wheel will be unchanged with respect to the standardconfiguration with blades having an axis of change in radial pitch, i.e.reproducing the configuration of the tuned cyclic symmetry.

This is of particular interest since the differences in tilt of the axisof rotation and/or of the blade between the first blade 21 and thesecond blade 22 may cause particularly pronounced deviations at theblade head 2, i.e. specifically in the area where the blades are themost loaded in a low speed flight condition and wherein the acousticsources are the most intense.

Actually, in this way, at a high speed, the blades have the same spatialposition around the bladed wheel, in particular as regards the portionof the blade useful during high altitude flight, but for the low speedoperating points, relevant for the acoustics, for which the blades 2have to be realigned, typically of the order of 25°, the modification ofthe pitch, although simultaneous for the first blade 21 and the secondblade 22, typically by a single command, gives the possibility ofobtaining spatial positions between the first blade 21 and the secondblade 22 within the bladed wheel.

According to an example, the second blade has zero tilt of the axis ofrotation and a zero blade tilt, the first blade having a non-zero tiltof the axis of rotation, typically towards the downstream side, and analso non-zero blade tilt, typically towards the downstream side in thelow speed pitch position, so that the first blade is tuned with thesecond blade in the low speed pitch position and untuned in a high speedpitch position.

FIG. 10 thus illustrates an example of a first blade 21 in a high speedpitch position, for which the cord A₃ is then not tilted with respect tothe radial axis A₂, so as to be tuned with a second blade 22 accordingto FIG. 8, but for which the axis of rotation A₁ is however tilted.Thus, the modification of the pitch position along the tilted axis ofrotation A₁ allows modification of the tilt of the cord A₃ of the firstblade 21 with respect to the second blade 22 and therefore obtaining anuntuned low speed position with respect to the second blade 22 accordingto FIG. 8.

Distribution of Said at Least One First Blade and of Said at Least OneSecond Blade

As indicated above, said at least one first blade 21 typically comprisesone or several first blades 21 and said at least one second blade 22comprises typically one or several second blades 22, which aredifferentiated by their tilt of the axis of rotation and/or their bladetilt as described herein before for at least one pitch.

The bladed wheel may comprise at least one third blade, typically one orseveral third blades, typically tilted in a fixed way so as to have athird tilt of the axis of rotation or of the blade axis which isdifferent from the first tilt and from the second tilt.

Thus, the bladed wheel may comprise several other sets of blades eachhaving a different tilt from that of the other sets of thereby definedblades.

The first blades 21 and the second blades 22 may be placed along thebladed wheel according to an untuned spatial organization as describedabove, giving the possibility of compensating for the dissymmetry of theresulting forces and therefore preventing imbalance problems.

Such a correction may for example comprise a periodic organization persectors of the first blades 21 and optionally of the second blades 22 soas to compensate for the variation of the forces on the untuned blades,i.e. the first blades 21, with respect to the standard blades, typicallythe second blades 22.

The blades 2 may be distributed uniformly with respect to each other atthe periphery of the bladed wheel.

The first blades 21 may be distributed uniformly with respect to eachother at the periphery of the bladed wheel.

With reference to FIG. 3c , a bladed wheel is described as describedearlier, for example comprising twelve blades 2, for which a portion,for example a quarter, of the blades of the plurality of blades 2 arefirst blades 21 which have a first tilt of the axis of rotation and/or afirst blade tilt as described earlier, the first tilt being differentfrom the second tilt of a portion of the other blades, for example ofall the other blades, for example the three quarters of the blades ofthe plurality of blades 2, these other blades being second blades 22.

The feet of the shafts of all the blades of the plurality of blade 2 arefor example distributed uniformly along the bladed wheel. The feet ofthe shafts of al the first blades of the plurality of blades 2 are forexample distributed uniformly around the engine axis. The first blades21 and the second blades 22 for example have identical geometricalshapes, the difference between the first blades 21 and the second blades22 resulting from the different tilt of their axis of rotation A₁ withrespect to the corresponding radial axis A₂ of each of the blades.

With reference to FIG. 3d , a bladed wheel is described, as describedearlier, comprising for example twelve blades 2, for which one portion,for example a third, of the blades of the plurality of blades 2 arefirst blades 21 which have a first tilt of the axis of rotation and/or afirst blade tilt as described earlier, this first tilt being differentfrom the second tilt of a portion of the other blades, for example ofall the other blades, for example of the two thirds of the blades of theplurality of blades 2, these other blades being second blades 22.

With reference to FIG. 4, a diagram is described representing the soundintensity (dB in ordinates) versus the blade passing frequency BPF inthe case of a bladed wheel according to the prior art as compared withthe case of a bladed wheel according to the invention, in particular abladed wheel according to FIG. 3 d.

It is noted that the distinction of the blades 2 of the bladed wheelbetween the first blades 21 and the second blades 22 gives thepossibility of reducing the perceived noise level. Indeed, in the priorart, all the identical blades positioned uniformly participate informing a tone component 420. With a bladed wheel according to theinvention, as the one described in FIG. 3d , the tone component 420 isreplaced, for at least one pitch, with several distinct tone componentsof lower levels, typically a first tone component 421 for the firstblades 21 which have a first tilt as described earlier and a second tonecomponent 422 for the second blades 22 having a second tilt as describedearlier, typically a second zero tilt. The result of this is a reductionin the perceived noise in the calculation of EPNL.

The periodicity of the blades 2 along the bladed wheel having beenmodified, the acoustic signature of the fundamental line will no longerbe localized on one frequency but at least on two.

The amplitude of each line of the untuned bladed wheel also tends todecrease since the specific noise being proportional to the load of theblading, the load of the blades signing on each distinct frequencydecreases.

This mechanism therefore gives the possibility, by applying it in arelevant way for generating the heterogeneity of the bladed wheel, ofdecreasing the value of the EPNL criterion, used for the acousticcertification of airplanes in a take-off and landing phase.

Associated Turbine Engine

The turbine engine may thus comprise such a bladed wheel with variablepitch. The turbine engine may in particular comprise two of such bladedwheels with variable pitch, the bladed wheels being for example contrarotative bladed wheels.

Turbine Engine with Two Bladed Wheels

Arrangement of the First Bladed Wheel and of the Second Bladed Wheel

The turbine engine may comprise a first bladed wheel 1000 as describedearlier.

With reference to FIG. 11, the turbine engine may further comprise asecond bladed wheel 2000. The second bladed wheel 2000 typicallycomprises a plurality of blades 2002. The first bladed wheel 1000 may bepositioned on the upstream side or on the downstream side of the secondbladed wheel 2000 along the axis of the turbine engine.

The first bladed wheel 1000 and the second bladed wheel 2000 typicallyhave different speeds and/or directions of rotation. The first bladedwheel 1000 and the second bladed wheel 2000 are typically contrarotative.

The first bladed wheel 1000 and the second bladed wheel 2000 may thus bepositioned with respect to each other so as to allow, during theoperation of the turbine engine, for example during a low speedoperation, a time and/or spatial phase shift of the interaction betweenthe first blade 21 and the blades 2002 of the second bladed wheel 2000and the interaction between the second blade 22 and the blades 2002 ofthe second bladed wheel 2000.

In the case of a turbine engine with two bladings positioned along theaxis of the turbine engine according to the prior art, the blades ofeach bladed wheel having the same tilt, typically in the case of anunducted fan and/or with contra rotative bladings, an interaction noiseresults from the operation of both bladings which is the consequence ofthe impact of the wakes 81 and of the vortices 82 from blades of thebladed wheel positioned upstream with the blades of the bladed wheelpositioned downstream.

This interaction noise is one of the main sources of the noise perceivedin the approach and take-off phases. This interaction noise is verypronounced, in particular in the case of turbine engines with anunducted fan and contra rotative bladed wheels, even more in theparticular case when all the blades are identical.

The interaction between the upstream and downstream bladings of theturbine engine is reproduced at each crossing between the blades of thebladed wheel upstream and of the bladed wheel downstream. The result ofthis is an acoustic signature marked on discrete frequenciescorresponding to combinations of the blade passing frequencies of thebladed wheel upstream and of the bladed wheel downstream of the typen*BPF₁+m*BPF₂ with BPF_(i) the blade passing frequency of the bladedwheel i as described earlier with n and m being natural integers.

This is most pronounced for the unducted fans, the noise of which isestimated as substantially greater than the one emitted by theconventional ducted fan. One of the reasons is the absence of a nacellesurrounding the bladed wheels, a nacelle which conventionally gives thepossibility of masking and/or attenuating a portion of the acousticradiation generated by the blades as well as the interaction phenomenamarked between the bladed wheels by the use of acoustic treatmentspositioned in the conduit, on the walls of the nacelle.

In order to reduce this interaction noise, the possibilitiesconventionally provided to one skilled in the art consist according tothe prior art of optimizing the identical aerodynamic profile for eachof the blades of a bladed wheel. This means acting on the intensity ofthe pressure fluctuations resulting from the interactions between blades2 by optimizing the shape of the profiles or the distribution of load onthe extension of the blade 2 in order to modify the influence of thehead vortex. For example, it is possible to avoid the impact of the headvortex of the upstream propeller with the blades of the downstreampropeller by truncating the latter but this is done to the detriment ofthe aerodynamic performances at a high speed. Further, the optimizationof the profiles for minimizing the wakes from the upstream bladed wheelon the critical operating points towards the acoustic certificationimplies a modification of the shape of the profiles by increasing theircurvature in order to reduce the incidence of work of the profiles onthese low speed mission points. This adaptation of the profiles intendedfor acoustics, goes against the aerodynamic optimization at a high speedfor which the transonic behavior of the profiles require a low curvatureof the latter.

The adaptations of the profiles according to known methods of the priorart for minimizing the interaction noise therefore prove to complex anddelicate since they impact in a detrimental way the high speed yield ofthe propellers thereby degrading the fuel consumption on a mission.

The turbine engine described here according to an exemplary embodimentof the invention with the first bladed wheel 1000 and the second bladedwheel 2000 gives the possibility of reducing the intensity of theinteraction noise by modifying aerodynamic interactions between thefirst bladed wheel 1000 and the second bladed wheel 2000.

It is thus possible to modify the space-time characteristics of theinteraction of the wakes from the bladed wheel positioned upstream withthe blades of the bladed wheel positioned downstream. This modificationof the interactions is accomplished by introducing the space and/or timephase shift of the interactions differentiating the influence from orreceived from the first blades 21 with respect to the second blades 22of the same first bladed wheel 1000.

If the first bladed wheel 1000 is positioned upstream, these areinfluences from the blades since the wakes stem from them. Thesedifferences in tilt give the possibility of generating different wakesbetween a first blade 21 and a second blade 22 so as to both generate adifferent interaction during the crossing with the blades of the secondbladed wheel 2000 downstream but also a space and/or time phase shiftwith respect to an identical interaction on all the blades 2 of thesecond bladed wheel 2000 downstream.

If the first bladed wheel 1000 is positioned downstream, these areinfluences received by the blades since the wakes from the second bladedwheel 2000 upstream interact differently with the first blades 21 andwith the second blades 22. These tilt differences give the possibilityto the wakes to generate different interactions between a first blade 21and a second blade 22 and a space and/or time phase shift with respectto an identical interaction on all the blades of the bladed wheeldownstream.

In both cases, this space-time phase shift may give the possibility ofreducing the global acoustic signature of the doublet of propellers byauthorizing different recombinations of the sound sources along thedirection of observation. A notable reduction in the perceived noiselevel may thus be obtained.

The upstream bladed wheel and the downstream bladed wheel may both havefirst bladed wheels 1000 as described earlier, i.e. that each comprisesat least one first blade 21 having a first tilt as indicated above andat least one second blade having a second tilt different from the firsttilt. It is thus possible to benefit from these tilt differences both onthe upstream bladed wheel and on the downstream bladed wheel in order toreduce by as much the perceived noise from each bladed wheelindividually like interactions between both bladed wheels.

As compared with configurations of the prior art, the turbine enginedescribed here allows spatial and time disorganization of theinteractions between the wakes from the upstream bladed wheel and theblades of the downstream bladed wheel. Such that disorganization allowsa potential reduction in the interaction noise at a lesser cost sincethe blades used for a same bladed wheel may remain with an identicalgeometrical shape. Thus, it is not necessary to produce two differentblade forms and it is not necessary to resort to a double referenceduring the mounting of the turbine engine.

Further, as described above, this untuning may only be substantiallyactive for flight configurations requiring a particular attention forthe acoustics, notably at a low speed.

Further, such a modification of the bladings is easy to apply since themodification of the space positioning of the blades within the bladedwheel at a low speed is simply produced by the rotation around the axisfor changing pitch having a tangential component and/or a componenttowards the upstream side or towards the downstream side. Thismodification of the space position is however performed withoutmodifying substantially the pitch of the profiles with constant radius,which ensures a minor modification of the aerodynamic operation.

Exemplary Embodiments

With reference to FIG. 12, contra rotative bladed wheels according tothe prior art and according to exemplary embodiments of the inventionare described, in the case when the upstream bladed wheel is the firstbladed wheel 1000 comprising at least a first blade 21 and at least asecond blade 22, the first blade 21 being for example positioned betweentwo second blades 22.

The first bladed wheel 1000 upstream rotates at a first speed and in afirst direction ω₁. The second bladed wheel 2000 rotates at a secondspeed and in a second direction ω₂ opposite to the first direction ω₁.

The first blade has two possible positions corresponding to two untuningexamples by the first tilt of the axis of rotation A₁. The blade 210represents the location for a bladed wheel of the prior art of the bladepositioned between the two second blades 22, at an equal distance fromboth and without its axis of rotation A₁ being tilted with respect tothe corresponding radial axis A₂.

According to the first example, the first blade 211 has a first tiltcomprising a tangential component β so as to be tilted rearwards withrespect to the direction of rotation of the first bladed wheel 1000.

According to the second example, the first blade 212 has a first tiltcomprising a tangential component β so as to be tilted forwards withrespect to the direction of rotation of the first bladed wheel 1000.

Two consecutive blades 2010 and 2020 of the second bladed wheel 2000downstream are also illustrated. The blades of the bladed wheel 2000 arefor example identical in shape and in tilt and uniformly distributed inan azimuthal way for the bladed wheel 2000, i.e. without any untuning.

The blade 2020 is illustrated at three instants t, t+Δt and t−Δt′ in theengine reference system.

Thus, the blade referenced as 2020 represents the blade 2020 at instantt, the blade 2010 and the first bladed wheel being also represented atinstant t. At this instant t, the wake from the non-tuned blade 210 ofthe upstream bladed wheel of the prior art would cross the blade 2020.

The blade referenced as 2021 represents the blade 2020 at instant t+Δt.At this instant t+Δt, the wake from the first blade 211 of the firstbladed wheel 1000 of the first example, which has a first tilt of theaxis of rotation of the blade comprising a tangential component βrearwards, crosses the blade 2020.

The blade referenced as 2022 represents the blade 2020 at the instantt−Δt′. At this instant t−Δt′, the wake from the first blade 212 of thefirst bladed wheel 1000 of the second example, which has a first tilt ofthe axis of rotation of the blade comprising a tangential component βforwards, crosses the blade 2020.

The blade 2020 of the second bladed wheel 2000 positioned downstream,thus crosses the wakes of the first blades 21 untuned of the firstbladed wheel 1000 positioned upstream or earlier (second example withthe first blade 212) or later (first example with the first blade 211)with respect to the crossing of a wake from a non-untuned blade 210.Therefore there is actually a time phase shift of the interactionbetween the first blades 21 of the first bladed wheel 1000 positionedupstream and the blades of the second bladed wheel 2000 positioneddownstream, which is expressed by a different interaction frequency.

The wakes from the blade 210 of the prior art, from the first blade 211and from the first blade 212 are different since although these bladesretain an incidence close because of their identical pitch, the volumesof the latter will be different on the one hand because of the tilt, theshown stacking is different, and on the other hand the path of the wakebefore impact on the upstream blade will be more or less long because ofthe first tilt which has a tangential component and/or a componenttowards the upstream side or towards the downstream side.

The pressure fluctuation resulting from the crossing of the blades ofthe first bladed wheel 1000 and of the second bladed wheel 2000 istherefore different according to the untuning of the first blades 21 andtherefore has a time phase shift which is also itself different.

Further, the crossing of the wake with the blades of the bladed wheeldownstream taking place at different instants (t t+Δt, t−Δt′), thepressure fluctuation will spatially occur at different positions of thebladed wheel downstream.

A phase shift of the acoustic sources from one blade to the other, onthe same bladed wheel, thereby ensures a potential reduction at theinteraction noise level.

The invention claimed is:
 1. A bladed wheel with variable pitchescomprising: a plurality of blades, each with a variable pitch along anaxis of rotation of a blade and each having a root, the plurality ofblades comprising a first blade and a second blade; and a plurality ofrotor connection shafts, each rotor connection shaft having a foot and ahead, the root of each blade being mounted on the head of acorresponding rotor connection shaft through a pivot so as to allow therotation of each blade along the blade rotation axis, wherein the firstblade has a first tilt of the axis of rotation, such that the bladerotation axis of the first blade is tilted in a fixed way with respectto a radial axis of the bladed wheel passing through the foot of thecorresponding rotor connection shaft, and the second blade has a secondtilt of the axis of rotation different from the first tilt of the axisof rotation so as to present an untuning between the first blade and thesecond blade for at least one pitch, wherein the first tilt of the axisof rotation comprises a tangential tilt component in a plane of thebladed wheel.
 2. The bladed wheel according to claim 1, wherein thefirst tilt of the axis of rotation comprises a tilt component towards anupstream or a downstream side with respect to a plane of a propeller. 3.The bladed wheel according to claim 1, wherein the axis of rotation ofthe second blade is fixed with respect to the corresponding radial axis.4. The bladed wheel according to claim 1, wherein each shaftcorresponding to the first blade is tilted with respect to the radialaxis, tilting the first corresponding blade according to the first tiltof the axis of rotation.
 5. The bladed wheel according to claim 1,wherein each shaft corresponding to the first blade has a joint tiltingthe head of the shaft with respect to a remainder of the shaft, and thustilting the first corresponding blade according to the first tilt of theaxis of rotation.
 6. The bladed wheel according to claim 1, wherein thefirst blade and the second blade have a same geometrical shape.
 7. Thebladed wheel according to claim 1, wherein the first blade has a firstblade tilt, such that the first blade is tilted in a fixed way withrespect to the blade rotation axis of the first blade, and the secondblade has a second blade tilt different from the first blade tilt. 8.The bladed wheel according to claim 7, wherein the first blade and thesecond blade are configured so that the respective pitches along thecorresponding blade axes of rotation are modified simultaneously, and sothat: when the bladed wheel is blocked in a high speed position, aposition of the first blade with respect to the corresponding radialaxis is the same as a position of the second blade with respect to thecorresponding radial axis, when the bladed wheel is blocked in a lowspeed position, the position of the first blade with respect to thecorresponding radial axis is different from the position of the secondblade with respect to the corresponding radial axis.
 9. The bladed wheelaccording to claim 1, wherein each pivot is mounted in an axisymmetricring including a plurality of substantially cylindrical housings,wherein roller bearings are positioned between the ring and each pivotso as to provide a degree of rotary freedom of the pivot with respect tothe ring, and wherein the first tilt of the axis of rotation of thefirst blade and the second tilt of the axis of rotation of the secondblade are applied to the roller bearings.
 10. A turbine enginecomprising a first bladed wheel according to claim
 1. 11. The turbineengine according to claim 10, further comprising a second bladed wheel,the second bladed wheel comprising a plurality of blades, the firstbladed wheel being positioned upstream or downstream from the secondbladed wheel along the axis of the turbine engine, so as to allow,during the operation of the turbine engine, at least one of a time orspace phase shift of an interaction between the first blade of the firstbladed wheel and the blades of the second bladed wheel, with respect toan interaction between the second blade of the first bladed wheel andthe blades of the second bladed wheel.
 12. The turbine engine accordingto claim 11, wherein the first bladed wheel and the second bladed wheelhave at least one of different speeds or directions of rotation.